Cold-storage heat exchanger

ABSTRACT

Provided is a cold-storage heat exchanger. The cold-storage heat exchanger includes a pair of header tanks, and tubes which are arranged in three rows with respect to the direction of the flow of air and connected at opposite sides thereof to the header tanks. A cold-storage medium is stored in the tubes that are disposed in a middle row, and refrigerant circulates through the tubes that are disposed in front and rear rows. Therefore, the cold-storage medium can effectively store cold-energy transferred from the refrigerant. When the engine of a vehicle is stopping, the cold-storage heat exchanger can discharge the cold-energy that has been stored into the passenger compartment of the vehicle, thus preventing the temperature in the passenger compartment from rapidly increasing, thereby creating pleasant air-conditioned conditions for a user, and minimizing the energy and time required to re-cool the passenger compartment.

TECHNICAL FIELD

The present invention relates to a cold-storage heat exchanger, and moreparticularly, to a cold-storage heat exchanger which includes a pair ofheader tanks each of which comprises three rows of parts with respect toa direction of the flow of air, and three rows of tubes that are fixedat opposite ends thereof to the header tanks, wherein a cold-storagemedium is stored in tubes disposed in a middle row, and refrigerantcirculates in front and rear rows of tubes so that cold-energy of therefrigerant can be effectively stored in the cold-storage medium, andwhen an engine of a vehicle is in a stopped state, the cold-energy isdischarged into the passenger compartment of the vehicle, thuspreventing the temperature in the passenger compartment from rapidlyincreasing, thereby creating pleasant air-conditioned conditions for auser, and minimizing the energy and time required to re-cool thepassenger compartment.

BACKGROUND ART

Recently, the growing interest in the environment and energy all overthe world is encouraging research into improving fuel efficiency in theautomobile industry. Research and development into reducing the weightand size and increasing performance have been being steadily conductedto fulfill different kinds of consumer demands. Particularly, researchand development into hybrid vehicles which use engine power and electricenergy together are increasing.

Many kinds of hybrid vehicles use an idle stop/go system in which anengine automatically stops when a vehicle stops, for example, whilewaiting for the light to change, and manipulating a transmissionrestarts the engine. However, because such a hybrid vehicle also usesthe engine to operate the air-conditioning apparatus, when the engine isstopping, a compressor also stops, increasing the temperature of anevaporator, resulting in making a user feel unpleasant. Furthermore,refrigerant in the evaporator easily evaporates even at roomtemperature. Hence, if the refrigerant evaporates during the time forwhich the compressor is not in operation, even though the engine isrestarted, and the compressor and the evaporate are re-operated, ittakes a relatively long time to supply cold air into the passengercompartment because it is necessary to compress the evaporatedrefrigerant and re-liquefy it. In addition, this causes the problem ofan increase of the overall energy consumption.

In an effort to improve air-conditioning efficiency, a related techniquewas proposed in Japanese Patent Laid-open Publication No. 2000-205777(entitled: Cold-storage heat exchanger). This technique is illustratedin FIG. 1.

As shown in FIG. 1, the cold-storage heat exchanger 90 includes tubes91, each of which has a double tube structure and is integrallyconfigured such that a refrigerant passage 91 e through whichrefrigerant flows and cold-storage-medium chambers 91 f and 91 f aredefined in the double-layered tube 91. Fluid passages 94 are formedbetween the tubes 91 an that heat can be transferred between therefrigerant and fluid passing through the fluid passages 94.

However, in the conventional cold-storage heat exchanger of FIG. 1,manufacturing the double-layered tube includes joining several sheets ofplates. Defective joining frequently occurs. The double tube structuremakes the manufacture of the tube difficult. The problem of defectivejoining is accompanied by a problem of the refrigerant mixing with thecold-storage medium. In addition, even if there is a defectively joinedportion, it is very difficult to find such a portion.

Moreover, although the conventional cold-storage heat exchanger has anadvantage in that the cold-storage medium receives cold energy from therefrigerant because the passage along which the refrigerant flows isdisposed at an inside position in the double tube structure while thecold-storage-medium chamber that stores the cold-storage medium isdisposed at an outside position in the double tube structure, thisdouble tube structure reduces the efficiency of heat transfer betweenthe refrigerant and air that passes over the outside of the double tubestructure and comes into contact with the cold-storage-medium chamber.Further, the fins that are disposed outside the double-layered tubesalso come into contact only with the cold-storage-medium chamber withoutmaking direct connect with the refrigerant passage. In addition, thisdouble tube structure restricts the size of the space in which thecold-storage medium can be stored, thus resulting in reducing the heatexchange efficiency.

FIG. 2 illustrates another conventional technique, showing a plate typecold-storage heat exchanger 80 which has a structure of three rows witha cold-storage medium stored in a middle row. In this cold-storage heatexchanger, a part for storing a cold-storage medium is disposed betweenfront and rear rows of tubes 81 each of which is formed by joiningplates 82. This conventional technique has the advantage of improvingthe efficiency with which cold energy of the refrigerant is stored inthe cold-storage medium, but given the characteristics of the platetype, it is difficult to provide a sufficient space for storing thecold-storage medium. Therefore, the amount of cold-storage medium isinsufficient, making it difficult to ensure satisfactory cold-energystorage performance. Furthermore, the durability and the corrosionresistance are comparatively low, reducing the lifetime of thecold-storage heat exchanger.

DISCLOSURE OF INVENTION Technical Problem

An object of the present invention is to provide a cold-storage heatexchanger in which a separate part for storing a cold-storage medium isprovided between front and rear rows of tubes so that cold energy ofrefrigerant can be effectively stored and, when the engine of a vehicleis in the stopped state, the cold energy that has been stored isdischarged into the passenger compartment, thus preventing thetemperature in the passenger compartment from rapidly increasing therebycreating pleasant air-conditioned conditions for a user, and minimizingthe energy and time required to re-cool the passenger compartment.

Another object of the present invention is to provide a cold-storageheat exchanger which uses tubes of the same height so that each fininterposed between the tubes can be integrally formed, thus enhancingthe productivity with which the cold-storage heat exchanger ismanufactured.

A further object of the present invention is to provide a cold-storageheat exchanger in which the cold-storage medium is disposed at thecentral portion of the exchanger, so that air conditioning can takeplace instantaneously immediately after an air conditioner has beenoperated, and in which the amount of cold-storage medium which can bestored is increased compared to that of the plate type cold-storage heatexchanger, so that the performance of storage of cold-energy can beenhanced.

Yet another object of the present invention is to provide a cold-storageheat exchanger in which a baffle is installed at a predeterminedposition in a header tank and partitions all of spaces of first, secondand third rows so that the refrigerant that is in the first and thirdrows of tubes can be prevented from mixing with the cold-storage mediumthat is stored in the second row of tubes, and a communication passageformed by the baffle defines a path along which the refrigerant flowsbetween the first and third rows, thus facilitating the formation of thecommunication passage.

Still another object of the present invention is to provide acold-storage system which can maintain the cold-storage medium, storedin the cold-storage part of the cold-storage heat exchanger, in a statesuitable for the function of storing cold-energy, and which can enhancethe performance of heat exchange and cold-energy storage of thecold-storage heat exchanger.

Solution to Problem

In one general aspect, a cold-storage heat exchanger includes: a firstheader tank and a second header tank provided parallel to each other atpositions spaced apart from each other by a predetermined distance, eachof the first and second header tanks having therein partitions extendingin a longitudinal direction so that a space in each of the first andsecond header tanks is partitioned with respect to a lateral directioninto three spaces comprising a first space, a second space and a thirdspace; a plurality of tubes arranged in three rows with respect to thelateral direction, the tubes comprising: refrigerant tubes through whichrefrigerant circulates, each of the refrigerant tubes being connected atopposite ends thereof to the first spaces of a first row or the thirdspaces of a third row; and a cold-storage tubes connected at oppositeends thereof to the second spaces of a second row, the cold-storagetubes storing a cold-storage medium therein; fins interposed between thetubes; and an inlet pipe and an outlet pipe each provided on the firstheader tank or the second header tank so that the refrigerant flows intothe cold-storage heat exchanger through the inlet pipe and flows outtherefrom through the outlet pipe.

Further, a refrigerant passing hole may be formed in a predeterminedportion of each of laterally-opposite sidewalls of the second space ofat least either the first header tank or the second header tank so thatthe first space communicates with the third space to allow therefrigerant to flow between the first space and the third space. Thecold-storage heat exchanger may further include partitioning means forisolating the refrigerant flowing between the first space and the thirdspace from the heat storage medium stored in the cold-storage tubes.

The second space may be partitioned with respect to a height directionby the partitioning means into a primary-second space and asecondary-second space formed above the primary-second space, whereinthe primary-second space may communicate with the cold-storage tubes,and the refrigerant passing holes may be disposed in thesecondary-second space.

The cold-storage heat exchanger may include:a first heat exchange partwhich the refrigerant circulates along the tubes that communicate withthe first spaces; a second heat exchange part in which the refrigerantcirculates along the tubes that communicate with the third spaces; and acold-storage part in which the cold-storage medium is stored in thetubes that communicate with the primary-second space.

The partitioning means may include a separate planar member extending inthe longitudinal direction so that the second space is partitioned intosections with respect to a height direction, wherein laterally-oppositeedges of the planar member may be bent so that the planar member isinstalled in the second space of the first header tank or the secondheader tank.

The partitioning means may have a shape of a tube connecting therefrigerant passing holes to each other.

Each of the inlet pipe and the outlet pipe may be connected to the firstspace or the third space of the first or second header tank.

The inlet pipe or the outlet pipe may communicate with thesecondary-second space of the first header tank or the second headertank.

The refrigerant passing holes may include: inflow branch holes formed inthe secondary-second space communicating with the inlet pipe; andoutflow branch holes formed in the secondary-second space communicatingwith the outlet pipe.

The inflow branch holes may be formed in the partitions disposed in anarea in which the refrigerant drawn into the inlet pipe branches offinto the first space and the third space. The outflow branch holes maybe formed in the partitions disposed in an area in which the refrigerantthat has passed through the first heat exchange part and the second heatexchange part is drawn into the first space and the third space anddischarged into the outlet pipe.

The inflow branch holes may comprise a first inflow branch holecommunicating with the first space, and a second inflow branch holecommunicating with the third space, and the outflow branch holes maycomprise a first outflow branch hole communicating with the first space,and a second outflow branch hole communicating with the third space,wherein the first inflow branch hole comprises at least one first inflowbranch hole, the second inflow branch hole comprises at least one secondinflow branch hole, the first outflow branch hole comprises at least onefirst outflow branch hole, and the second outflow branch hole comprisesat least one second outflow branch hole.

The cold-storage heat exchanger may further include: a pipe connectorprovided on an outer surface of one side with respect to thelongitudinal direction of the cold-storage heat exchanger, the pipeconnector comprising: a first pipe connector communicating with thesecondary-second space formed in either the first header tank or thesecond header tank, so that the refrigerant flows through the first pipeconnector, the first pipe connector being connected to the inlet pipe;and a second pipe connector communicating with the secondary-secondspace formed in a remaining one of the first header tank and the secondheader tank, so that the refrigerant flows through the second pipeconnector, the second pipe connector being connected to the outlet pipe.

The first pipe connector and the second pipe connector may be configuredsuch that the inlet pipe and the outlet pipe are disposed parallel toeach other at positions adjacent to each other.

The cold-storage heat exchanger may further include: a first pipedisposed outside the first header tank and provided parallel to thefirst header tank in the longitudinal direction; a second pipe disposedoutside the second header tank and provided parallel to the secondheader tank in the longitudinal direction; a primary-first branch pipeand a secondary-first branch pipe branching off from the first pipe, theprimary-first branch pipe extending to the first space of the firstheader tank while the secondary-first branch pipe extends to the thirdspace of the first header tank; and a primary-second branch pipe and asecondary-second branch pipe branching off from the second pipe, theprimary-second branch pipe extending to the first space of the secondheader tank while the secondary-second branch pipe extends to the thirdspace of the second header tank, wherein the first pipe is connected toeither the inlet pipe or the outlet pipe, and the second pipe isconnected to a remaining one of the inlet pipe or the outlet pipe, sothat the refrigerant flows into one of the first pipe and the secondpipe or out of a remaining one of the first pipe and the second pipe.

The cold-storage heat exchanger may further include: partitioning meansprovided in either the first header tank or the second header tank, thepartitioning means for partitioning the first space, the second spaceand the third space with respect to the longitudinal direction to definea partitioned section in each of the first, second and third spaces,wherein the refrigerant passing holes are disposed in the second spacein the partitioned section defined by the partitioning means, and therefrigerant flows through the cold-storage tubes and the refrigeranttubes that are disposed at positions corresponding to the partitionedsections of the first, second and third spaces, the partitioned sectionsbeing defined by the partitioning means and having the refrigerantpassing holes therein.

The partitioning means may be configured such that a number of lines oftubes disposed at the positions corresponding to the partitionedsections is at least one and is 25% or less of total lines of tubes.

The cold-storage heat exchanger may further include a sealing baffleprovided at a position adjacent to each of openings, the openings beingformed in opposite ends of each of the first header tank and the secondheader tank, or an end cap sealing each of the openings.

A cold-storage-medium injection hole may be formed in the second spaceso that the cold storage medium is injected into the second spacethrough the cold-storage-medium injection hole.

Each of the first header tank and the second header tank may be formedby coupling a header to a tank cover plate, each of the header and thetank cover plate being formed by extruding, wherein the partitions areprovided in the header or the tank cover plate so that the space in eachof the first and second header tanks is partitioned into the firstspace, the second space and the third space, and the partitioning meansis formed in the second space in the longitudinal direction byintegrally extruding the partitioning means with the header or the tankcover plate.

Each of the first header tank and the second header tank may be formedby integrally extruding a header and a tank cover plate, the header andtank cover plate defining the first space, the second space and thethird space, and the partitioning means may be formed in the secondspace in the longitudinal direction by integrally extruding thepartitioning means with the header or the tank cover plate.

The tubes arranged in the three rows may be integrally extruded at asame time.

The fins interposed between the tubes arranged in the three rows may beintegrally formed.

In another general aspect, a cold-storage system having the cold-storageheat exchanger includes: a reservoir storing a cold-storage medium; acirculation pump circulating the cold-storage medium between thereservoir and cold-storage tubes of the cold-storage heat exchanger; acontrol unit controlling the circulation pump; and a circulation pipeconnecting the reservoir, the circulation pump and the cold-storagetubes of the cold-storage heat exchanger to one another.

Advantageous Effects of Invention

In a cold-storage heat exchanger according to the present invention, aseparate part for storing a cold-storage medium is provided betweenfront and rear rows of tubes. Therefore, the cold energy of arefrigerant can be effectively stored. When the engine of a vehicle isin the stopped state, the cold energy that has been stored is dischargedinto the passenger compartment, thus preventing the temperature in thepassenger compartment from rapidly increasing thereby creating pleasantair-conditioned conditions for a user, and minimizing the energy andtime required to re-cool the passenger compartment of the vehicle.

Furthermore, the cold-storage heat exchanger uses the tubes of the sameheight so that each fin interposed between the tubes can be integrallyformed, thus enhancing the productivity with which the cold-storage heatexchanger is manufactured.

In addition, the cold-storage medium is disposed at the central portionof the exchanger. Thus, air conditioning can take place instantaneouslyimmediately after an air conditioner has been operated. The amount ofcold-storage medium which can be stored is increased compared to that ofthe plate type cold-storage heat exchanger, so that the performance ofthe storage of cold-energy can be enhanced.

Moreover, a baffle is installed at a predetermined position in a headertank and partitions all of spaces of the first, second and third rows sothat the refrigerant that is in the first and third rows of tubes can beprevented from mixing with the cold-storage medium that is stored in thesecond row of tubes. Further, a communication passage formed by thebaffle defines a path along which the refrigerant flows between thefirst and third rows, thus facilitating the formation of thecommunication passage along.

A cold-storage system including the cold-storage heat exchangeraccording to the present invention can maintain the cold-storage medium,stored in the cold-storage part of the cold-storage heat exchanger, in astate suitable for the function of storing cold-energy. Further, thecold-storage system can enhance the performance of heat exchange and theperformance of cold-energy storage of the cold-storage heat exchanger.

BRIEF DESCRIPTION OF DRAWINGS

The above and other objects, features and advantages of the presentinvention will become apparent from the following description ofpreferred embodiments given in conjunction with the accompanyingdrawings, in which:

FIG. 1 is a perspective view of a conventional cold-storage heatexchanger having a double pipe structure;

FIG. 2 is a perspective view of a conventional plate type cold-storageheat exchanger;

FIGS. 3 through 5 are respectively a perspective view, an explodedperspective view and a front view illustrating a cold-storage heatexchanger, according to an embodiment of the present invention;

FIGS. 6 and 7 are respectively an exploded perspective view and a frontview illustrating a cold-storage heat exchanger, according to anotherembodiment of the present invention;

FIG. 8 is an exploded perspective view illustrating a cold-storage heatexchanger, according to a further embodiment of the present invention;

FIGS. 9 through 13 are views showing several embodiments of a path alongwhich a heat exchanging medium circulates in the cold-storage heatexchanger of the present invention;

FIG. 14 is a front view illustrating a cold-storage heat exchanger,according to yet another embodiment of the present invention;

FIG. 15 is a perspective view illustrating a cold-storage heatexchanger, according to still another embodiment of the presentinvention;

FIGS. 16 through 18 are respectively a perspective view, an explodedperspective view and a front view illustrating a cold-storage heatexchanger, according to still another embodiment of the presentinvention;

FIGS. 19 and 20 are respectively an exploded perspective view and afront view illustrating a cold-storage heat exchanger, according tostill another embodiment of the present invention;

FIGS. 21 through 26 are views showing several embodiments of a pathalong which a heat exchanging medium circulates in the cold-storage heatexchanger of the present invention;

FIG. 27 is a perspective view illustrating a cold-storage heatexchanger, according to stilt another embodiment of the presentinvention;

FIG. 28 is a perspective view illustrating a cold-storage heatexchanger, according to still another embodiment of the presentinvention;

FIG. 29 is a view showing the construction of a cold-storage systemincluding the cold-storage heat exchanger according to the presentinvention;

FIGS. 30 through 32 are respectively a perspective view, an explodedperspective and a front view illustrating a cold-storage heat exchanger,according to still another embodiment of the present invention;

FIGS. 33 and 34 are respectively an exploded perspective view and afront view illustrating a cold-storage heat exchanger, according tostill another embodiment of the present invention;

FIG. 35 is an exploded perspective view illustrating a cold-storage heatexchanger, according to still another embodiment of the presentinvention; and

FIGS. 36 through 39 are views showing several embodiments of a pathalong winch a heat exchanging medium circulates in the cold-storage heatexchanger of the present invention.

1: cold-storage system 2: reservoir 3: circulation pump 4: control unit5: circulation pipe 10: cold-storage heat exchanger 100, 200: firstheader tank, second header tank 110: header 120: tank cover plate 130:opening 310, 320, 330: first space, second space, third space 321:primary-second space 322: secondary-second space 340: refrigerantpassing hole 350: inflow branch hole 351, 352: first inflow branch hole,second inflow branch hole 360: outflow branch hole 361, 362: firstoutflow branch hole, second outflow branch hole 370: partition 380:cold-storage-medium injection hole 390: stopper 400: tube 410, 430:refrigerant tube 420: cold-storage tube 440: fin 510, 520: inlet pipe,outlet pipe 610: partitioning means 620: baffle 630: sealing baffle 640:insert slot 650: coupling slot 660: end cap 710, 720, 730: first heatexchange part, second heat exchange part, cold-storage part 741, 742:first flow path, second flow path 800: pipe connector 810, 820: firstpipe connector, second pipe connector 910, 920: first pipe, second pipe911, 912: primary-first branch pipe, secondary-first branch pipe 921,922: primary-second branch pipe, secondary-second branch pipe

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, the embodiments of the present invention will be describedin detail with reference to the accompanying drawings.

A cold-storage heat exchanger 10 according to the present inventionincludes a first header tank 100, a second header tank 200, tubes 400,fins 440, an inlet pipe 510 and an outlet pipe 520.

Particularly, as shown in FIG. 7, the first header tank 100 and thesecond header tank 200 of the cold-storage heat exchanger 10 are spacedapart from each other by a predetermined distance in the heightdirection and are parallel to each other. The internal space of each ofthe first and second header tanks 100 and 200 is separated into threespaces with respect to the lateral direction by partitions 370 which areprovided in the header tank 100, 200 and extend in the longitudinaldirection. The three spaces comprise a first space 310, a second space320 and a third space 330.

The tubes 400 are arranged in three rows in the lateral direction. Thetubes 400 comprise refrigerant tubes 410 and 430 which are respectivelyfixed at opposite ends thereof to the first and third spaces 310 and 330and allow refrigerant to circulate through them, and cold-storage tubes420 which are fixed at opposite ends thereof to the second spaces 320and in which a cold-storage medium is stored.

The cold-storage heat exchanger 10 is preferably configured such thatthe tubes 400 that are arranged in three rows have the same height,width and shape.

Furthermore, when manufacturing the cold-storage heat exchanger 10, thetubes 400 that are arranged in three rows may be formed by extruding atthe same time and may be integrally connected to each other. In thiscase, the manufacture and assembly of cold-storage heat exchanger 10 canbe facilitated.

The fins 440 are interposed between the tubes 400, wherein each fin 440is interposed between corresponding two of the tubes 400 that arearranged in three rows and is integrally formed, so that heat exchangebetween the cold-storage tube 420 and the refrigerant tubes 410 and 430can be conducted by the fins 440. Further, the integrated structure ofthe fin 440 facilitates its manufacture.

The cold-storage heat exchanger 10 of the present invention may furtherinclude a baffle 620 which is provided in each of the first and thirdspaces 310 and 330 to control the flow of refrigerant.

Particularly, in the cold-storage heat exchanger 10 of the presentinvention, a refrigerant passing hole 340 is formed in a predeterminedportion of each of laterally-opposite sidewalk of the second space 320of either the first header tank 100 or the second header tank 200 sothat the first space 310 can communicate with the third space 330 toallow the refrigerant to flow between the first and third spaces 310 and330. The cold-storage heat exchanger 10 further includes a separatepartitioning means 610 that isolates the refrigerant that flows betweenthe first space 310 and the third space 330 from the heat storage mediumstored in the cold-storage tubes 420.

Thereby, in the cold-storage heat exchanger 10 of the present invention,the refrigerant can circulate through the refrigerant tubes 410 and 430without being mixed with the heat storage medium stored in thecold-storage tubes 420.

As shown in FIGS. 4 and 5 illustrating an embodiment of the cold-storageheat exchanger 10 of the present invention, each of the first and secondheader tanks 100 and 200 may be formed by coupling a header 110 and atank cover plate 120 to each other. Here, each of the header 110 and thetank cover plate 120 has an integrated structure. The partitions 370that extend in the longitudinal direction are provided in either theheader 110 or the tank cover plate 120 so that the internal space of theheader tank 100, 200 is partitioned into the first space 310, the secondspace 320 and the third space 330.

As shown in FIG. 5, the partitions 370 may protrude from the innersurface of the header 110. Alternatively, the partitions 370 may beprovided in the tank cover plate 120.

Each of the header 110 and the tank cover plate 120 can be formed by apressing process. The header 110 and the tank cover plate 120 are brazedto each other, forming the first header tank 100 or the second headertank 200.

In each of the first and second header tanks 100 and 200, tube insertholes 111 are formed in the header 110 by a cutting or pressing processso that the tubes 400 are inserted into the header 110 through the tubeinsert holes 111. The refrigerant passing hole 340 is formed in each ofthe partitions 370 that are provided in either the header 110 or thetank cover plate 120. In this state, the header 110 and the tank coverplate 120 are coupled to each other, forming the first header tank 100or the second header tank 200.

Furthermore, as shown in FIGS. 6 and 7 illustrating another embodimentof the cold-storage heat exchanger 10, each of the first and secondheader tanks 100 and 200 may he formed in such a way that a header 110and a tank cover plate 120 which form each of the first space 310, thesecond space 320 and the third space 330 are integrally extruded into asingle structure, and the three integrally-extruded structures arearranged in three rows and then coupled to each other.

That is, each of the first space 310, the second space 320 and the thirdspace 330 is formed by integrally forming the corresponding header 110and tank cover plate 120. The structures which separately define thefirst, second and third spaces 310, 320 and 330 are arranged in threerows and coupled to each other, thus forming the first header tank 100or the second header tank 200.

Furthermore, each of the first header tank 100 and the second headertank 200 may be formed by integrally extruding the header 110, the tankcover plate 120 and the partitions 370. In this case, in each of thefirst header tank 100 and the second header tank 200, the refrigerantpassing hole 340 may be formed by a separate process in each of thepartitions 370 that partition the internal space of the header tank 100,200 into the first space 310, the second space 320 and the third space330.

Means for coupling the structures defining the first, second and thirdspaces 310, 320 and 330 to each other may be welding, and as well aswelding, there can be many different kinds of means.

The cold-storage heat exchanger having the above-mentionedcharacteristics can be embodied in embodiments 1 through 9.

Embodiment 1

As shown in FIGS. 3 through 7, the cold-storage heat exchanger 10 of thepresent invention may include a partitioning means 610 which comprises aplanar member extending in the longitudinal direction and partitions thesecond space 320 into two portions with respect to the height direction,wherein the second space 320 is partitioned by the partitioning means610 into a primary-second space 321 which communicates with thecold-storage tubes 420 and a secondary-second space 322 which allows therefrigerant to circulate through the refrigerant passing holes 340.

In this embodiment, laterally-opposite edges of the partitioning means610 are bent so that the partitioning means 610 can be installed in thesecond space 320 of the first header tank 100 or the second header tank200. The partitioning means 610 can be installed in the second space 320in such a way that it is longitudinally inserted into the second space320.

Preferably, the length of the partitioning means 610 is the same as thatof the second space 320.

Furthermore, it is not necessary for the partitioning means 610 to havea U shape in which the opposite edges thereof are bent. In other words,the partitioning means 610 can have any shape, so long as it canpartition the second space 320 into two separate spaces.

In this embodiment of the cold-storage heat exchanger 10, thepartitioning means 610 isolates the primary-second space 321 from thesecondary-second space 322 so that the refrigerant can pass between thefirst space 310, the secondary-second space 322 and the third space 330through the refrigerant passing holes 340.

Similarly, as shown in FIG. 14, the cold-storage heat exchanger 10 maybe configured such that the partitioning means 610 comprises a planarpart that is integrally formed with the partitions 370 which protrudefrom the inner surface of the tank cover plate 120.

In the cold-storage heat exchanger 10 of this case, the tank cover plate120 can be integrally extruded with the partitions 370 and thepartitioning means 610.

Alternatively, each of the first header tank 100 and the second headertank 200 may be formed in such a way that the header 110, the tank coverplate 120, the partitioning means 610 and the partitions 370 areintegrally formed by extruding. In this case, the refrigerant passingholes 340 may be formed by a separate process in the predeterminedportions of the respective partitions 370 that are disposed in thesecondary-second space 322, so that the first space 310 and the thirdspace 330 communicate with each other through the refrigerant passingholes 340.

Embodiment 2

As shown in FIG. 8, the partitioning means 610 of the cold-storage heatexchanger 10 according to the preset invention may comprise a tubularpartitioning, means 610 which connects the refrigerant passing holes 340to each other.

In the cold-storage heat exchanger 10 of this embodiment, the tubularpartitioning means 610, which connects the refrigerant passing holes 340that are formed in the laterally-opposite sidewalls of the second space320 to each other, forms a passage for circulation of refrigerantbetween the first space 310 and the third space 330.

In this case, the passage for circulation of refrigerant can be easilyformed using the partitioning means 610 in the second space 320 of thecold-storage heat exchanger 10.

Embodiment 3

In the cold-storage heat exchanger 10 of the present invention, eitherthe inlet pipe 510 through which the refrigerant enters the cold-storageheat exchanger 10 or the outlet pipe 520 through which the refrigerantis discharged therefrom communicates with one of the first space 310 andthe third space 330, and the other one of the inlet pipe 510 and theoutlet pipe 520 communicates with the other one of the first space 310and the third space 330.

Preferably, the inlet pipe 510 is disposed on one of the first and thirdspaces 310 and 330 that is disposed in the front row with respect to thedirection of the flow of air, while the outlet pipe 520 is disposed onthe other one of the first and third spaces 310 and 330 that is disposedin the rear row with respect to the direction of airflow.

In the cold-storage heat exchanger 10, the path along which therefrigerant circulates through the refrigerant tubes 410 and 430 can bevariously changed depending on the locations of the inlet pipe 510, theoutlet pipe 520 and the baffles 620. FIGS. 9 through 13 illustratedifferent examples of the path along which refrigerant circulates.Hereinafter, for the sake of explanation, it will be assumed that theheader tank that is disposed at the upper position in the drawings isthe first header tank 100, the header tank that is disposed at the lowerposition in the drawings is the second header tank 200, and the firstspace 310, the second space 320 and the third space 330 are arranged inorder with respect to the direction of airflow.

The flow path of refrigerant in the cold-storage heat exchanger 10 shownin FIG. 9 will now be explained.

FIG. 9 illustrates the case where the inlet pipe 510 and the outlet pipe520 are disposed on different sides of the cold-storage heat exchanger10. Refrigerant is drawn into the cold-storage heat exchanger 10 throughthe inlet pipe 510 that communicates with the first space 310 of thefirst header tank 100. The drawn refrigerant moves downwards along thecorresponding refrigerant tubes 410 that are fixed at the opposite endsthereof to the first spaces 310 of the first and second header tanks 100and 200. Subsequently, the refrigerant passes through the first space310 of the second header tank 200 and moves upwards again along thecorresponding refrigerant tubes 410. Thereafter, the refrigerant entersthe third space 330 of the first header tank 100 through the refrigerantpassing holes 340 that are formed in the first space 310 and the thirdspace 330 of the first header tank 100.

Subsequently the refrigerant moves downwards along the correspondingrefrigerant tubes 430 that are fixed at the opposite ends thereof to thethird spaces 330 of the first and second header tanks 100 and 200. Therefrigerant passes through the third space 330 of the second header tank200 and then moves upwards again and enters the third space 330 of thefirst header tank 100. The refrigerant is thereafter discharged out ofthe cold-storage heat exchanger 10 through the outlet pipe 520 thatcommunicates with the third space 330 of the first header tank 100.

In other words, the cold-storage heat exchanger 10 is configured suchthat refrigerant is drawn into the first space 310 and then dischargedout of the cold-storage heat exchanger 10 via the third space 330. Here,the partitioning means 610 functions to prevent the refrigerant frombeing mixed with the cold-storage medium that is stored in thecold-storage tubes 420 that are fixed at the opposite ends of the secondspaces 320 of the first and second header tanks 100 and 200.

Therefore, in the cold-storage heat exchanger 10, cold energy of therefrigerant, which circulates through the first and third rows of tubes400 that are disposed at opposite sides in the direction of airflow, istransferred to and stored in the cold-storage medium that is disposed inthe second row of tubes 400. Thereby, the cold-storage performance canbe enhanced, so that a pleasant air-conditioned environment can beeffectively maintained.

The flow of refrigerant in the cold-storage heat exchanger 10 of FIG. 10will now be explained.

FIG. 10 illustrates the case where the inlet pipe 510 and the outletpipe 520 are disposed on the same side of the cold-storage heatexchanger 10. Refrigerant is drawn into the cold-storage heat exchanger10 through the inlet pipe 510 that communicates with the first space 310of the first header tank 100. The drawn refrigerant moves downwardsalong the corresponding refrigerant tubes 410 and then enters the thirdspace 330 of the second header tank 200 via the refrigerant passingholes 340 that are formed in the first space 310 and the third space 330of the second header tank 200.

Thereafter, the refrigerant passes through the third space 330 of thesecond header tank 200 and then moves upwards again and enters the thirdspace 330 of the first header tank 100. Subsequently, the refrigerant isdischarged out of the cold-storage heat exchanger 10 through the outletpipe 520 that communicates with the third space 330 of the first headertank 100.

The flow of refrigerant in the cold-storage heat exchanger 10 of FIG. 11will now be explained, showing another example of the path ofcirculation of refrigerant. Refrigerant is drawn into the cold-storageheat exchanger 10 through the inlet pipe 510 that communicates with thefirst space 310 of the first header tank 100. The drawn refrigerantmoves downwards along the corresponding refrigerant tubes 410, passesthrough the first space 310 of the second header tank 200, moves upwardsagain, and then enters the third space 330 of the first header tank 100via the refrigerant passing holes 340 that are formed in the first space310 and the third space 330 of the first header tank 100.

Subsequently, the refrigerant moves downwards along the correspondingrefrigerant tubes 430 that are fixed at the opposite ends thereof to thethird spaces 330 of the first and second header tanks 100 and 200.Thereafter, the refrigerant flows along the third space 330 of thesecond header tank 200, moves upwards again, and then enters the thirdspace 330 of the first header tank 100. Subsequently, the refrigerant isdischarged out of the cold-storage heat exchanger 10 through the outletpipe 520 that communicates with the third space 330 of the first headertank 100.

The flow of refrigerant in the cold-storage heat exchanger 10 of FIG. 12will now be explained, showing a further example of the path ofcirculation of refrigerant. Refrigerant is drawn into the cold-storageheat exchanger 10 through the inlet pipe 510 that communicates with thefirst space 310 of the first header tank 100. The drawn refrigerantflows along the corresponding refrigerant tubes 410 in an up and downzigzag manner and then goes back to the first space 310 of the firstheader tank 100. Subsequently, the refrigerant flows into the thirdspace 330 through the refrigerant passing holes 340 that are formed inthe first space 310 and the third space 330 of the first header tank100.

Thereafter, the refrigerant flows in an up and down zigzag manner alongthe corresponding refrigerant tubes 430 that are fixed at the oppositeends thereof to the third space 330, and then reaches again the thirdspace 330 of the first header tank 100. The refrigerant is subsequentlydischarged out of the cold-storage heat exchanger 10 through the outletpipe 520 that communicates with the third space 330 of the first headertank 100.

An example of the path of circulation of refrigerant, shown in FIG. 13,is similar to the example of FIG. 12, but in the example of FIG. 13, therefrigerant passing holes are formed in the first and third spaces 310and 330 of the second header tank 200, unlike that of the example ofFIG. 12.

Embodiment 4

Referring to FIG. 15, in the cold-storage heat exchanger 10 according tothe present invention, a cold-storage medium is stored in thecold-storage tube 420, wherein of the second spaces 320 of the first andsecond header tanks 100 and 200 to which the opposite ends of thecold-storage tubes 420 are fixed, a cold-storage-medium injection hole380 is formed in the second space 320 other than the second space 320that has the partitioning means 610 and the refrigerant passing hole 340therein, so that the sold-storage medium is injected into thecorresponding second space 320 through the cold-storage-medium injectionhole 380.

The cold-storage-medium injection hole 380 is closed by a stopper 390.After the cold-storage medium has been injected into the second space320, the cold-storage-medium injection hole 380 is sealed with thestopper 390. As necessary, after the injection, the cold-storage-mediuminjection hole 380 may be permanently sealed by means of welding or thelike.

Embodiment 5

As shown in FIGS. 17 through 20, the cold-storage heat exchanger 10according to this embodiment of the present invention includes apartitioning means 610 which comprises a planar member extending in thelongitudinal direction and partitions each second space 320 into twoportions with respect to the height direction. The cold-storage heatexchanger 10 includes a first heat exchange part 710 in whichrefrigerant circulates along the tubes 400 that communicate with thefirst spaces 310, a second heat exchange part 720 in which refrigerantcirculates along the tubes 400 that communicate with the third spaces330, and a cold-storage part 730 in which a cold-storage medium isstored in the tubes 400 that communicate with a primary-second space321.

In the cold-storage heat exchanger 10 according to this embodiment,either an inlet pipe 510 or an outlet pipe 520 communicates with asecondary-second space 322 of one of the first and second header tanks100 and 200, and the other one of the inlet pipe 510 and the outlet pipe520 communicates with a secondary-second space 322 of the other one ofthe first and second header tanks 100 and 200. Hereinafter, the casewill be described with reference to FIGS. 16 through 26, which assumethat the header tank that is disposed at the upper position in thedrawings is the first header tank 100, and the header tank that isdisposed at the lower position in the drawings is the second header tank200.

In this embodiment, refrigerant passing holes 340 comprise inflow branchholes 350 which are formed in the secondary-second space 322 thatcommunicates with the inlet pipe 510, and outflow branch holes 360 whichare formed in the secondary-second space 322 that communicates with theoutlet pipe 520.

That is, the inflow branch holes 350 are formed in the partitions 370 ofthe secondary-second space 322 of the first header tank 100 so that therefrigerant that has been drawn into the secondary-second space 322 ofthe first header tank 100 through the inlet pipe 510 branches off intothe first space 310 and the third space 330 through the inflow branchholes 350.

Furthermore, the outflow branch holes 360 are formed in the partitions370 of the secondary-second space 322 of the second header tank 200 sothat the refrigerant that has circulated through the first heat exchangepart 710 and the second heat exchange part 720 flows front the firstspace 310 and the third space 330 into the secondary-second space 322 ofthe second header tank 200 through the outflow branch holes 360 beforebeing discharged out of the cold-storage heat exchanger 10 through theoutlet pipe 520.

The inflow branch holes 350 comprise a first inflow branch hole 351which communicates with the first space 310 of the first header tank100, and a second inflow branch hole 352 which communicates with thethird space 330 of the first header tank 100. The outflow branch holes360 comprise a first outflow branch hole 361 which communicates with thefirst space 310 of the second header tank 200, and a second outflowbranch hole 362 which communicates with the third space 330 of thesecond header tank 200.

As shown in FIG. 21, in the cold-storage heat exchanger 10 according tothis embodiment, a first flow path 741 along which the refrigerantcirculates in the first heat exchange part 710 is independently formedfrom a second flow path 742 along which the refrigerant circulates inthe second heat exchange part 720. The type of circulation path formedby each of the first flow path 741 and the second flow path 742 is thesame type of path.

The flow of the refrigerant will now be explained with reference to FIG.21.

The refrigerant flows into the cold-storage heat exchanger 10 throughthe inlet pipe 510 that communicates with the secondary-second space 322of the first header tank 100. Some of the refrigerant that has drawninto the secondary-second space 322 flows into the second heat exchangepart 720 through the second inflow branch hole 352, and the remainingrefrigerant flows into the first heat exchange part 710 through thefirst inflow branch hole 351.

The refrigerant that has been drawn into the second heat exchange part720 flows downwards along the corresponding tubes 400, enters the thirdspace 330 of the second header tank 200, and then flows upwards againunder the guidance of the baffle 620 that is provided in the third space330.

Thereafter, the refrigerant enters the third space 330 of the firstheader tank 100, flows downwards again under the guidance of the baffle620 that is provided in the third space 330 of the first header tank100, and then reaches the third space 330 of the second header tank 200,thus completing the circulation in the second heat exchange part 720.Subsequently, the refrigerant flows into the secondary-second space 322of the second header tank 200 through the second outflow branch hole362.

The refrigerant that has been drawn into the first heat exchange part710 also flows in an up and down zigzag manner similar to the path ofcirculation of the refrigerant that has been drawn into the second heatexchange part 720, and then enters the secondary-second space 322 of thesecond header tank 200 through the first outflow branch hole 361.Thereafter, the refrigerant, along with the refrigerant that has enteredsecondary-second space 322 of the second header tank 200 through thesecond outflow branch hole 362, is discharged out of the cold-storageheat exchanger 10 through the outlet pipe 520.

As such, in the cold-storage heat exchanger 10, the first flow path 741and the second flow path 742 form independent circulation paths, thusenhancing the efficiency of heat exchange between the air and therefrigerant that circulates along the first flow path 741 and the secondflow path 742. When it is in an idle stop/go state, the cold-storagepart 730 discharges cold air that has been stored therein into thepassenger compartment of the vehicle, thus preventing the temperature inthe passenger compartment from rapidly increasing, thereby reducing theconsumption of power to operate the compressor, and contributing toincreasing the fuel efficiency.

As shown in FIG. 23, the cold-storage heat exchanger 10 may beconfigured such that the first flow path 741 along which the refrigerantcirculates in the first heat exchange part 710 is independently formedfrom the second flow path 742 along which the refrigerant circulates inthe second heat exchange part 720, wherein the first flow path 741 andthe second flow path 742 each form a different type of circulation pathrelative to the other.

The flow of the refrigerant will now be explained with reference to FIG.23.

The refrigerant flows into the cold-storage heat exchanger 10 throughthe inlet pipe 510 that communicates with the secondary-second space 322of the first header tank 100. Some of the refrigerant that has beendrawn into the secondary-second space 322 flows into the second heatexchange part 720 through the second inflow branch hole 352, and theremaining refrigerant flows into the first heat exchange part 710through the first inflow branch hole 351.

The refrigerant that has been drawn into the second heat exchange part720 flows downwards along the corresponding tubes 400, enters the thirdspace 330 of the second header tank 200, and then flows upwards againunder the guidance of the baffle 620 that is provided in the third space330.

Thereafter, the refrigerant enters the third space 330 of the firstheader tank 100, flows downwards again under the guidance of the baffle620 that is provided in the third space 330 of the first header tank100, and then reaches the third space 330 of the second header tank 200,thus completing the circulation in the second heat exchange part 720.Subsequently, the refrigerant flows into the secondary-second space 322of the second header tank 200 through the second outflow branch hole362.

Meanwhile, the refrigerant that has entered the first heat exchange part710 flows downwards, enters the first space 310 of the second headertank 200, and flows into the secondary-second space 322 of the secondheader tank 200 through the first outflow branch hole 361. Thereafter,the refrigerant, along with the refrigerant that has entered thesecondary-second space 322 of the second header tank 200 through thesecond outflow branch hole 362, is discharged out of the cold-storageheat exchanger 10 through the outlet pipe 520.

In this case, the first flow path 741 and the second flow path 742 formindependent circulation paths along which the refrigerant circulateswhile heat exchange takes place between it and the air, whereas thefirst flow path 741 and the second flow path 742 form different types ofcirculation paths, so that cold energy of the cold-storage part 730 canbe effectively transferred to the refrigerant. Furthermore, theindependent circulation paths are configured such that they intersecteach other so that the overall temperature distribution can be madeuniform.

As shown in FIG. 24, the cold-storage heat exchanger 10 may beconfigured such that each of the first flow path 741 and the second flowpath 742 forms a single path style rather than forming a zigzag typepath so that the pressure of working fluid can be prevented from beingreduced, and such that the first and second flow paths 741 and 742 thatare the independent circulation paths intersect each other to make theoverall temperature distribution uniform.

Furthermore, the cold-storage heat exchanger 10 may be configured suchthat each of the first inflow branch hole 351, the second inflow branchhole 352, the first outflow branch hole 361 and the second outflowbranch hole 362 comprises at least one or more, that is, a plurality ofholes, so that the flow paths of the refrigerant are formed as shown inFIGS. 25 and 26.

The flow of the refrigerant in the cold-storage heat exchanger 10 ofFIG. 25 will now be explained.

The refrigerant flows into the cold-storage heat exchanger 10 throughthe inlet pipe 510 that communicates with the secondary-second space 322of the first header tank 100. Some of the refrigerant that has beendrawn into the secondary-second space 322 flows into the second heatexchange part 720 through the second inflow branch hole 352, and theremaining refrigerant flows into the first heat exchange part 710through the first inflow branch holes 351.

In this case, the two first inflow branch holes 351 are formed in thesecondary-second space 322 of the first header tank 100 at positionsspaced apart from each other by a predetermined distance in thelongitudinal direction so that the refrigerant can be distributed intotwo portions of the first heat exchange part 710.

Some of the refrigerant that has entered the first heat exchange part710 through the corresponding one of the first inflow branch holes 351flows downwards along the corresponding tubes 400, enters the firstspace 310 of the second header tank 200, and then flows upwards againunder the guidance of a baffle 620 that is provided in the first space310 of the second header tank 200.

Thereafter, the refrigerant that has reached the first space 310 of thefirst header tank 100 is mixed with the remaining refrigerant that hasentered the first heat exchange part 710 through the other first inflowbranch hole 351, and the mixed refrigerant flows downwards again underthe guidance of a baffle 620 that is provided in the first space 310 ofthe first header tank 100 and reaches the first space 310 of the secondheader tank 200, thus completing the circulation in the first heatexchange part 710. Subsequently, the refrigerant enters thesecondary-second space 322 of the second header tank 200 through thefirst outflow branch hole 361.

The refrigerant that has entered the second heat exchange part 720 alsoflows in an up and down zigzag manner similar to the path of circulationof the refrigerant that has entered the first heat exchange part 710,and then enters the secondary-second space 322 of the second header tank200 through the second outflow branch hole 362. Subsequently, therefrigerant, along with the refrigerant that has entered thesecondary-second space 322 of the second header tank 200 through thefirst outflow branch hole 361, is discharged out of the cold-storageheat exchanger 10 through the outlet pipe 520.

As shown in FIG. 26, the second outflow branch hole 362 may comprise twosecond outflow branch holes 362 which are formed in the secondary-secondspace 322 of the second header tank 200 at positions spaced apart fromeach other by a predetermined in the longitudinal direction. In thiscase, the refrigerant that flows through the third space 330 of thesecond header tank 200 branches off into two streams along the twosecond outflow branch holes 362 and enters the secondary-second space322 before being discharged out of the cold-storage heat exchanger 10through the outlet pipe 520.

Embodiment 6

The cold-storage heat exchanger 10 according to this embodiment has thesame first flow path 741 and second flow path 742 as those of FIG. 21 ofthe fifth embodiment, whereas as shown in FIG. 22, in the sixembodiment, the outlet pipe 520 is disposed at a position adjacent tothe inlet pipe 510 outside the cold-storage heat exchanger 10. In thiscase, the pipe layout and packaging of an HVAC (Heating, Ventilation andAir Conditioning) system can be facilitated so that the space in thevehicle can be effectively utilized.

To achieve the above purpose, as shown in FIG. 28, the cold-storage heatexchanger 10 may further include a pipe connector 800 which is providedon the outer surface of the cold-storage heat exchanger 10 at one sidewith respect to the longitudinal direction and comprises a first pipeconnector 810 and a second pipe connector 820. The first pipe connector810 communicates with either the first header tank 100 or the secondheader tank 200, so the refrigerant flows through the first pipeconnector 810. The inlet pipe 100 is provided on the first pipeconnector 810. The second pipe connector 820 communicates with the otherone of the first header tank 100 and the second header tank 200, so therefrigerant flows through the second pipe connector 820. The outlet pipe520 is provided on the second pipe connector 820.

In the cold-storage heat exchanger 10 of this case, the first pipeconnector 810 and the second pipe connector 820 are configured such thatthe inlet pipe 510 and the outlet pipe 520 are disposed adjacent to eachother and are parallel to each other.

Further, the pipe connector 800 communicates only with thesecondary-second space 322 but not with the primary-second space 321 sothat the refrigerant can be isolated from the cold-storage medium.

Each the first and second pipe connectors 810 and 820 of the pipeconnector 800 may be configured such that the shape thereof is that of atank which defines space therein or alternatively, it is formed bycoupling a separate plate to the exchanger.

Embodiment 7

As shown in FIG. 27, in the cold-storage heat exchanger 10 according tothis embodiment, a first pipe 910 is provided on the upper surface ofthe first header tank 100 and extends in the longitudinal direction ofthe first header tank 100. Furthermore, at least one primary-firstbranch pipe 911 and at least one secondary-first branch pipe 912 branchoff from the first pipe 910 and communicate with the first space 310 andthe space 330, respectively.

The first pipe 910 is connected to the inlet pipe 510 so that therefrigerant is drawn into the first pipe 910 through the inlet pipe 510.The drawn refrigerant branches off into two streams, one entering thefirst space 310 through the primary-first branch pipe 911, and the otherentering the third space 330 through the secondary-first branch pipe912.

Preferably, a plurality of primary-first branch pipes 911 and aplurality of secondary-first branch pipes 912 are provided.

In the same manner, a second pipe 920 is provided under the lowersurface of the second header tank 200 and extends in the longitudinaldirection of the second header tank 200. Furthermore, at least oneprimary-second branch pipe 921 and at least one secondary-second branchpipe 922 branch off from the second pipe 920 and communicate with thefirst space 310 and the space 330 of the second header tank 200,respectively.

The second pipe 920 is connected to the outlet pipe 520. Thus, therefrigerant that has passed through the first heat exchange part 710 andreached the first space 310 of the second header tank 200 is dischargedinto the second pipe 920 through the primary-second branch pipe 921.

In addition, the refrigerant that has passed through the second heatexchange part 720 and reached the first space 310 of the second headertank 200 is discharged into the second pipe 920 through thesecondary-second branch pipe 922. Eventually, the refrigerant that haspassed through the secondary-second branch pipe 922 mixes with therefrigerant that has passed through the primary-second branch pipe 921,and then the mixed refrigerant is discharged out of the cold-storageheat exchanger 10 through the outlet pipe 520.

Embodiment 8

As shown in FIGS. 30 through 39, in the cold-storage heat exchangeraccording to this embodiment of the present invention, the inlet pipe510 and the outlet pipe 520 are respectively connected to the firstspace 310 and the third space 330.

Particularly, the cold-storage heat exchanger 10 according to thisembodiment includes a partitioning means 610 which is provided in eitherthe first header tank 100 or the second header tank 200 and partitionseach of the first space 310, the second space 320 and the third space330 with respect to the longitudinal direction to define a separatepartitioned section in each space 310, 320, 330. Furthermore, arefrigerant passing hole 340 is formed in a predetermined portion ofeach of laterally-opposite sidewalls of the separate partitioned sectionof the second space 320 so that the first space 310 can communicate withthe third space 330 so that the refrigerant can flow between the firstand third spaces 310 and 330.

Furthermore, in this cold-storage heat exchanger 10, refrigerant flowsthrough the first and third rows of refrigerant tubes 410 and 430 whichare respectively disposed at the front and rear rows with respect to thedirection of the flow of air. A cold-storage medium is stored in thesecond row of tubes 420 which is disposed between the first and thirdrows of tubes 410 and 430, wherein refrigerant flows through all thefirst, second and third rows of tubes 400 that are disposed at positionscorresponding to the separate partitioned sections of the first, secondand third spaces 310, 320 and 330 that are defined by the partitioningmeans 610 and have the refrigerant passing holes 340 therein.

Thereby, refrigerant can flow from the first row of refrigerant tubes410 to the third row of refrigerant tubes 410 through the refrigerantpassing holes 340 that are disposed in the separate partitioned sectionsdefined by the partitioning means 610. During this refrigerant flowprocess, the refrigerant can be prevented from mixing with thecold-medium medium that is stored in the second row of tubes 420.

In this embodiment, if there is one line of tubes 400 in the separatepartitioned sections of the first, second and third spaces 310, 320 and330 that are defined by the partitioning means 610 and have therefrigerant passing holes 340 therein, it is difficult to form thepartition structure. If 25% of the total lines of tubes 400 or more arein the separate partitioned sections, the size of the space that canstore the cold-storage medium is excessively reduced, deteriorating thecold-storage performance. Therefore, it is preferable for the positionof the partitioning means 610 to be determined such that the number oflines of tubes 400 disposed at positions corresponding to the separatepartitioned sections is at least one and is 25% or less of the totallines of tubes 400.

As shown in FIGS. 33 and 34, the cold-storage heat exchanger 10according to this embodiment may be configured such that an opening 130is formed in each of the opposite ends of the first and second headertanks 100 and 200, and a sealing baffle 630 is provided at a positionadjacent to each opening 130 to seal the opening 130, and a partitioningmeans 610 has the same shape as that of the sealing baffle 630.

In this case, insert slots 640 are formed in predetermined portions ofthe outer surfaces of the first header tank 100 and the second headertank 200 so that each of the sealing baffles 630 and the partitioningmeans 610 can be inserted into the first header tank 100 or the secondheader tank 200 through the corresponding insert slot 640. After thesealing baffles 630 and partitioning means 610 have been inserted intoand installed in the first and second header tanks 100 and 200, they arefor example brazed to the corresponding portions of the first and secondheader tanks 100 and 200.

Preferably, the sealing baffles 630 and the partitioning means 610 havethe same shape, and each of them has coupling slots 650 which are fittedover the outer sidewalls of the assemblies of the headers 110 and thetank cover plates 120 that define the first, second and third space 310,320 and 330, in other words, which are fitted over the junction surfacesbetween the assemblies that are arranged in three rows.

Of course, in the case where the headers 110 and the tank cover plates120 are integrally formed and the partitions 370 separate the first,second and third spaces 310, 320 and 330 from each other, coupling slots650 may be depressed in each of the sealing baffles 630 and thepartitioning means 610 to the depths corresponding to the heights of thecorresponding partitions 370 so that the sealing baffles 630 and thepartitioning means 610 can be fitted over the partitions 370 through thecoupling slots 650.

Furthermore, in the case where the headers 110 and the tank cover plates120 are integrally formed and the partitions 370 separate the first,second and third spaces 310, 320 and 330 from each other, the firstheader tank 100 and/or the second header tank 200 may be formed in sucha way that the sealing baffles 630 and the partitioning means 610 aredisposed in and fixed to the header 100 or the tank cover plate 120before the header 100 and the tank cover plate 120 are assembled witheach other, without the insert slots 640 being separately formed in theouter surface of the head tank 100, 200.

Meanwhile, as shown in FIG. 30, the cold-storage heat exchanger 10 ofthe present invention may include end caps 660 which seal the openings130 which are formed in the opposite ends of each of the first headertank 100 and the second header tank 200.

In the cold-storage heat exchanger 10 according to this embodiment thepath along which the refrigerant circulates through the refrigeranttubes 410 and 430 can be variously changed depending on the locations ofthe inlet pipe 510, the outlet pipe 520 and the baffles 620. FIGS. 36through 39 illustrate different examples of the path along whichrefrigerant circulates. Hereinafter, for the sake of explanation, itwill be assumed that the header tank that is disposed at the upperposition in the drawings is the first header tank 100, the header tankthat is disposed at the lower position in the drawings is the secondheader tank 200, the first row of refrigerant tubes 410, the second rowof cold-storage tubes 420 and the third row of refrigerant tubes 430 arearranged in order with respect to the direction of airflow, and thefirst space 310, the second space 320 and the third space 330 are alsoarranged in order with respect to the direction of airflow.

The flow path of refrigerant in the cold-storage heat exchanger 10 shownin FIG. 36 will now be explained.

In the cold-storage heat exchanger 10 of FIG. 36, refrigerant is drawninto the cold-storage heat exchanger 10 through the inlet pipe 510connected to the first space 310 of the first header tank 100. The drawnrefrigerant moves downwards along the first row of refrigerant tubes 410and flows into the third space 330 of the second header tank 200 throughthe refrigerant passing holes 340 formed in the second header tank 200.

Thereafter, the refrigerant passes through the third space 330 of thesecond header tank 200, moves upwards again, and enters the third space330 of the first header tank 100. Subsequently, the refrigerant isdischarged out of the cold-storage heat exchanger 10 through the outletpipe 520 connected to the third space 330 of the first header tank 100.

Here, a partitioning means 610 is installed in the second space 320 ofthe first header tank 100 at the same position as that in the secondspace 320 of the second header tank 200 so that the cold-storage mediumcan be prevented from mixing with the refrigerant.

In other words, the cold-storage heat exchanger 10 of FIG. 36 isconfigured such that the refrigerant is drawn into the first space 310of the first header tank 100 and discharged from the third space 330 ofthe first header tank 100. Here, thanks to the partitioning means 610that is provided in the second space 320 so that the cold-storage mediumcan be prevented from mixing with the refrigerant, the refrigerant canflow from the first space 310 into the third space 330 through therefrigerant passing holes 340 without giving rise to the problem ofbeing mixed with the cold-storage medium.

Therefore, in the cold-storage heat exchanger 10, cold energy of therefrigerant, which circulates through the refrigerant tubes 410 and 430that are disposed at opposite sides in the direction of airflow, istransferred to and stored in the cold-storage medium that is disposed inthe second row of cold-storage tubes 420. Thereby, the cold-storageperformance can be enhanced, so that a pleasant air-conditionedenvironment can be effectively maintained.

The flow of refrigerant in the cold-storage heat exchanger 10 of FIG. 37will now be explained, showing another example of the path ofcirculation of refrigerant. Refrigerant is drawn into the cold-storageheat exchanger 10 through the inlet pipe 510 connected to the firstspace 310 of the first header tank 100. The drawn refrigerant movesdownwards along the refrigerant tubes 410. The refrigerant thereafterpasses through the first space 310 of the second header tank 200, movesupwards again, and then flows into the third space 330 of the firstheader tank 100 through the refrigerant passing holes 340 formed in thefirst header tank 100.

Subsequently, the refrigerant flows downwards along the third row ofrefrigerant tubes 430 that are fixed at the opposite ends thereof to thethird spaces 330 of the first and second header tanks 100 and 200.Thereafter, the refrigerant passes through the third space 330 of thesecond header tank 200, moves upwards again, and then enters the thirdspace 330 of the first header tank 100. The refrigerant is subsequentlydischarged out of the cold-storage heat exchanger 10 through the outletpipe 520 connected to the third space 330 of the first header tank 100.

The flow of refrigerant in the cold-storage heat exchanger 10 of FIG. 38will now be explained, showing a further example of the path ofcirculation of refrigerant. Refrigerant is drawn into the cold-storageheat exchanger 10 through the inlet pipe 510 that communicates with thefirst space 310 of the first header tank 100. The drawn refrigerantflows along the corresponding refrigerant tubes 410 in an up and downzigzag manner and then reaches again the first space 310 of the firstheader tank 100. Subsequently, the refrigerant flows into the thirdspace 330 of the first header tank 100 through the refrigerant passingholes 340 that are formed in the first header tank 100.

Thereafter, the refrigerant flows in an up and down zigzag manner alongthe corresponding refrigerant tube 430 that are fixed at the oppositeends thereof to the third spaces 330 of the first and second headertanks 100 and 200, and then reaches the third space 330 of the firstheader tank 100. Subsequently, the refrigerant is discharged out of thecold-storage heat exchanger 10 through the outlet pipe 520 that isconnected to the third space 330 of the first header tank 100.

An example of the cold-storage heat exchanger 10 that is illustrated inFIG. 39 is similar to the example of FIG. 38, but in the example of FIG.39, the number of turns of the zigzag flow path is less than that of theexample of FIG. 38, and the refrigerant passing holes are formed in thefirst and third spaces 310 and 330 of the second header tank 200, unlikethat of the example of FIG. 39.

As described above, in the cold-storage heat exchanger 10 of the presentinvention, the circulation path of the refrigerant can be changeddepending on the locations of the inlet pipe 510, the outlet pipe 520,the refrigerant passing holes and the baffles 620 that are provided inthe first spaces 310 and the third spaces 330.

Embodiment 9

As shown in FIG. 29, a cold-storage system 1 including the cold-storageheat exchanger 10 having the above-mentioned construction comprises areservoir 2, a circulation pump 3, a control unit 4 and a circulationpipe 5. The reservoir 2 stores the cold-storage medium. The circulationpump 3 circulates the cold-storage medium between the reservoir 2 andthe cold-storage tubes 420 of the cold-storage heat exchanger 10. Thecontrol unit 4 controls the circulation pump 3. The circulation pipe 5connects the reservoir 2, the circulation pump 3 and the cold-storagetubes 420 of the cold-storage heat exchanger 10 to one another.

The cold-storage system 1 includes the cold-storage heat exchanger 10,and the elements of the cold-storage system 1 that are disposed outsidethe cold-storage heat exchanger 10 function to circulate thecold-storage medium that is stored in the cold-storage tubes 420.

In the cold-storage system 1, to circulate the cold-storage medium thathas been stored in the cold-storage part 730 of the cold-storage heatexchanger 10, the control unit 4 receives information about thetemperature and flow rate and operates the circulation pump 3 so thatthe cold-storage medium that has been stored in the cold-storage part730 is discharged from the cold-storage part 730 while freshcold-storage medium that has been in the reservoir 2 is charged into thecold-storage part 730.

The circulation pipe 5 is connected to the second spaces 320 which aredisposed in the middle rows of the first header tank 100 and the secondheader tank 200 of the cold-storage heat exchanger 10.

Therefore, the cold-storage system 1 having the above-mentionedconstruction can maintain the state of the cold-storage medium suitablefor the cold-storage function, thereby enhancing the performance of heatexchange and cold-storage of the cold-storage heat exchanger 10.

Although the preferred embodiments of the present invention have beendisclosed for illustrative purposes, those skilled in the art willappreciate that various modifications, additions and substitutions arepossible, without departing from the scope and spirit of the inventionas disclosed in the accompanying claims.

The invention claimed is:
 1. A cold-storage heat exchanger, comprising:a first header tank and a second header tank provided parallel to eachother at positions spaced apart from each other by a predetermineddistance, each of the first and second header tanks having thereinpartitions extending in a longitudinal direction so that a space in eachof the first and second header tanks is partitioned with respect to alateral direction into three spaces comprising a first space, a secondspace and a third space; a plurality of tubes arranged in three rowswith respect to the lateral direction, the tubes comprising: refrigeranttubes, through which refrigerant circulates, each of the refrigeranttubes, being connected at opposite ends thereof to the first space of afirst row or the third space of a third row; and a cold-storage tubeconnected at opposite ends thereof to the second space of a second row,the cold-storage tube storing a cold-storage medium therein; a fininterposed between the tubes; an inlet pipe and an outlet pipe eachprovided on the first header tank or the second header tank so that therefrigerant flows into the cold-storage heat exchanger through the inletpipe and flows out therefrom through the outlet pipe; refrigerantpassing holes each disposed in a predetermined portion of each oflaterally-opposite sidewalls of the second space of at least either thefirst header tank or the second header tank so that the first spacecommunicates with the third space to allow the refrigerant to flowbetween the first space and the third space; and a partitioning meanshaving a shape of a tube and connecting the refrigerant passing holes toeach other to isolate the refrigerant flowing between the first spaceand the third space from the cold-storage medium stored in thecold-storage tube.
 2. The cold-storage heat exchanger of claim 1,wherein each of the inlet pipe and the outlet pipe is formed at thefirst space or the third space of the first header tank or the secondheader tank.
 3. The cold-storage heat exchanger of claim 1, furthercomprising; a sealing baffle provided at a position adjacent to each ofopenings, the openings being formed in opposite ends of each of thefirst header tank and the second header tank; or an end cap sealing eachof the openings.
 4. The cold-storage heat exchanger of claim 1, whereina cold-storage-medium injection hole is formed in the second space sothat the cold storage medium is injected into the second space throughthe cold-storage-medium injection hole.
 5. The cold-storage heatexchanger of claim 1, wherein the tubes arranged in the three rows areintegrally formed by extruding at a same time.
 6. The cold-storage heatexchanger of claim 1, wherein the fin interposed between the tubesarranged in the three rows is integrally formed.
 7. A cold-storage heatexchanger, comprising: a first header tank and a second header tankprovided parallel to each other at positions spaced apart from eachother by a predetermined distance, each of the first and second headertanks having therein partitions extending in a longitudinal direction sothat a space in each of the first and second header tanks is partitionedwith respect to a lateral direction into three spaces comprising a firstspace, a second space and a third space; a plurality of tubes arrangedin three rows with respect to the lateral direction, the tubescomprising: refrigerant tubes, through which refrigerant circulates,each of the refrigerant tubes, being connected at opposite ends thereofto the first space of a first row or the third space of a third row; anda cold-storage tube connected at opposite ends thereof to the secondspace of a second row, the cold-storage tube storing a cold-storagemedium therein; a fin interposed between the tubes; an inlet pipe and anoutlet pipe each provided on the first header tank or the second headertank so that the refrigerant flows into the cold-storage heat exchangerthrough the inlet pipe and flows out therefrom through the outlet pipe;partitioning means provided in either the first header tank or thesecond header tank, the partitioning means for partitioning the firstspace, the second space and the third space with respect to thelongitudinal direction; and refrigerant passing holes each disposed in apredetermined portion of each of laterally-opposite sidewalls of thesecond space in a longitudinally partitioned section defined by thepartitioning means.
 8. The cold-storage heat exchanger of claim 7,wherein the refrigerant flows through the cold-storage tube and therefrigerant tubes, that are disposed at partitioned positions beingdefined by the partitioning means and having the refrigerant passinghole therein.
 9. The cold-storage heat exchanger of claim 7, wherein thepartitioning means is configured such that the number of lines of thetubes disposed at positions corresponding to the longitudinallypartitioned section being defined by the partitioning means and havingthe refrigerant passing holes therein is at least one and is 25% or lessof total lines of the tubes.
 10. The cold-storage heat exchanger ofclaim 7, wherein each of the inlet pipe and the outlet pipe is connectedto the first space or the third space of the first header tank or thesecond header tank.
 11. The cold-storage heat exchanger of claim 7,further comprising; a sealing baffle provided at a position adjacent toeach of openings, the openings being formed in opposite ends of each ofthe first header tank and the second header tank, or an end cap sealingeach of the openings.
 12. The cold-storage heat exchanger of claim 7,wherein a cold-storage-medium injection hole is formed in the secondspace so that the cold storage medium is injected into the second spacethrough the cold-storage-medium injection hole.
 13. The cold-storageheat exchanger of claim 7, wherein the tubes arranged in the three rowsare integrally formed by extruding at a same time.
 14. The cold-storageheat exchanger of claim 7, wherein the fin 440 interposed between thetubes arranged in the three rows is integrally formed.